EP2692481A1 - Dispositif de traitement par rayonnement - Google Patents

Dispositif de traitement par rayonnement Download PDF

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Publication number
EP2692481A1
EP2692481A1 EP12179304.6A EP12179304A EP2692481A1 EP 2692481 A1 EP2692481 A1 EP 2692481A1 EP 12179304 A EP12179304 A EP 12179304A EP 2692481 A1 EP2692481 A1 EP 2692481A1
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EP
European Patent Office
Prior art keywords
drive
platform
counterweight
displacement element
linear axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12179304.6A
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German (de)
English (en)
Inventor
Sergio Bossoni
Thomas Seiler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bystronic Laser AG
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Bystronic Laser AG
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Filing date
Publication date
Application filed by Bystronic Laser AG filed Critical Bystronic Laser AG
Priority to EP12179304.6A priority Critical patent/EP2692481A1/fr
Publication of EP2692481A1 publication Critical patent/EP2692481A1/fr
Withdrawn legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K37/00—Auxiliary devices or processes, not specially adapted to a procedure covered by only one of the preceding main groups
    • B23K37/02—Carriages for supporting the welding or cutting element
    • B23K37/0211—Carriages for supporting the welding or cutting element travelling on a guide member, e.g. rail, track
    • B23K37/0235—Carriages for supporting the welding or cutting element travelling on a guide member, e.g. rail, track the guide member forming part of a portal
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K37/00—Auxiliary devices or processes, not specially adapted to a procedure covered by only one of the preceding main groups
    • B23K37/02—Carriages for supporting the welding or cutting element
    • B23K37/0241—Attachments between the welding or cutting element and the carriage

Definitions

  • the invention relates to a beam processing apparatus, in particular a laser beam processing apparatus or a fluid jet processing apparatus having a first platform, with a second platform movably mounted on the first platform, with a beam processing head held by the second platform for processing a workpiece with a beam.
  • the second platform is connected to the first platform via a first displacement element and a second displacement element and the first displacement element is displaceably mounted on the first platform along a first linear axis and the second displacement element is displaceably mounted on the first platform along a second linear axis, wherein the first linear axis and the second linear axis are inclined to each other, preferably by 90 °.
  • the second platform is displaceably mounted on the first displacement element along a third linear axis and slidably mounted on the second displacement element along a fourth linear axis, wherein the first linear axis and the fourth linear axis substantially parallel to each other and stand and the second linear axis and the third linear axis substantially run or stand parallel to each other.
  • the beam-processing device has a first drive, which cooperates with the first displacement element to move the first displacement element relative to the first platform along the first linear axis, and a second drive, which cooperates with the second displacement element, to the second displacement element relative to the first Platform along the second linear axis to proceed.
  • the beam processing device has a first counterweight, which is displaceably mounted on the first platform along a fifth linear axis, and a second counterweight, which is displaceably mounted on the first platform along a sixth linear axis, wherein the first linear axis and the fifth linear axis substantially run parallel to each other or stand and run the second linear axis and the sixth linear axis substantially parallel to each other or stand.
  • a compensation of the disturbing forces can be done with additional drives.
  • the disturbance forces caused by the superimposed axes can be compensated by a force precontrol on the larger subordinate axes.
  • this requires very dynamic main-axle drives with additional power and a very complex control system.
  • the machine structure is unnecessarily excited with high-frequency loads, which can lead to increased demands on the machine structure or less good path accuracy.
  • the EP1294544B1 (equals to US7886629B2 ) discloses a Cartesian parallel kinematic drive for a laser processing machine (with major axes and superimposed axes in the XY direction). Countermeasures are in this Reference only casually mentioned, this document contains neither a doctrine about whether the countermeasures refer to the vertical axis or the horizontal axes, nor a lesson about their involvement in the kinematic system.
  • EP2283963A1 discloses a drive for a laser processing machine with a semi-redundant kinematics, in which only one axis is superimposed. A mass balance is not provided. The disturbing forces due to superimposed acceleration of the cutting head impair the movement of the carrier.
  • the EP1724054B1 a Cartesian, parallel kinematic system with counterweights for a machine tool.
  • the respective counterweight is driven by its own drive.
  • the disadvantage of such a solution is that the mass of the overall arrangement is enormously increased by the additional drives, whereby acceleration and inertia-related disturbances or a reduction in the dynamics are accompanied.
  • this solution requires a control engineering synchronization of the separate drives, which is expensive and maintenance-intensive.
  • the measures for a precisely matched, synchronized control of the drives for the jet machining head on the one hand and for the countermeasures on the other hand are also costly and error-prone.
  • EP1724054B1 Similar to EP1724054B1 are the W02006075209A2 (equivalent to US7910857B2 ), the EP1838486A1 and the EP1793963B1 each with separate drives for laser head and counterweights.
  • the EP1758003B1 discloses a method of handling a processing machine with redundant actuators using predetermined motion sequences. Counterweights are not provided.
  • the DE102009039201 B3 discloses for measuring and machine tools impulse decoupling in connection with the superposition of slow and fast axes of motion.
  • the DE102009039203A1 applies to measuring and machine tools compensation of torques.
  • disturbance forces and disturbance torques are compensated by additional two drives per axis.
  • a total of four drives per degree of freedom are needed, namely the first for the main axis, the second for the superimposed axis, the third and the fourth for the compensation of disturbing forces and moments.
  • the US7767932B2 discloses a laser cutting machine with polar drive, which is superimposed on a linear axis of movement.
  • the laser exit nozzle is linearly movable along this movement axis.
  • a rotary drive acts on a spindle, on one arm of the laser head and on the other arm, the counterweight sits. This approach is complicated because the heavy drive is located in the middle of the linear axis or in the axis of rotation of the polar drive.
  • JP1193134A discloses, in the context of a slide table for a workpiece, moving the table and a counterweight through a circulating traction means.
  • the EP1312441A1 discloses a machine tool with a spindle head which is displaceable along orthogonal guides, and with oppositely displaceable counterweights. This is a serial kinematics.
  • the forces resulting from the acceleration of masses should be optimally compensated for and, as a consequence, mechanical disturbances such as vibrations prevented.
  • the solution should also be characterized by simple construction and cost manufacturability.
  • the first drive is designed to move the first counterweight relative to the first platform along the fifth linear axis, wherein between the first displacement element and the first counterweight, a first mechanical coupling mechanism is switched, which is a method of the first displacement element when the first drive (including the second platform and beam processing head) and the first counterweight causes in mutually opposite directions, and / or the second drive is adapted to move the second counterweight relative to the second platform along the sixth linear axis, wherein between the second displacement element and the second counterweight a second mechanical coupling mechanism is connected, which, when the second drive is actuated, effects a movement of the second displacement element (together with the second platform and the jet machining head) and the second counterweight in mutually opposite directions.
  • a first mechanical coupling mechanism is switched, which is a method of the first displacement element when the first drive (including the second platform and beam processing head) and the first counterweight causes in mutually opposite directions
  • / or the second drive is adapted to move the second counterweight relative to the second platform along the sixth linear axis
  • the same drive which drives the respective displacement element, also causes the movement of the corresponding counterweight in the opposite direction.
  • a corresponding mechanical coupling mechanism ensures that the Displacement element and the counterweight in opposite directions (ie simultaneously movable in opposite directions) are synchronized. Such synchronization is far more reliable and less prone to error and allows high dynamics.
  • the present invention significantly reduces the overall weight and the number of components of a shot blast machine with respect to the prior art, without sacrificing machining precision.
  • the invention relates in particular to a Cartesian drive of a jet machining head with preferably parallel kinematic connection between the first and the second platform, countermeasures driven simultaneously and by the same drive being moved in the opposite direction to the jet machining head or to the respective displacement element in order to achieve mass balance achieve. Due to the mechanical coupling of a tool unit with the cutting head and in the opposite direction moving countermeasures, the disturbing forces can be minimized.
  • the first drive and / or the second drive is a rotary drive, preferably a torque motor.
  • the first drive and / or the second drive is a linear drive.
  • Linear actuators make it possible to arrange them not only on the first platform but also on other moving components, such as on a sliding element or on a counterweight.
  • Such drives can themselves serve as counterweight or as part of the counterweight and be integrated into the construction. Furthermore, such drives are characterized by their space-saving design.
  • the first drive on the first platform and / or the second drive is arranged on the first platform.
  • the drives are stationary with respect to the first platform and, together with the displacement elements, constitute a parallel kinematic drive.
  • the first drive forms at least part of the first counterweight and / or at least part of the second drive forms at least part of the second counterweight.
  • the total weight of the shot-blasting apparatus is further reduced since the respective one Drive not only performs the function of driving the sliding element and counterweight, but at the same time forms at least a portion of the counterweight.
  • the drive is accordingly displaceable as counterweight or as part of the counterweight relative to the first platform (along the fifth or sixth linear axis).
  • the drive interacts with the first platform insofar as the drive interacts with a structure of the first platform via a driven actuator end (eg a rotatable pinion) or acts on a structure of the first platform.
  • This structure may be, for example, a rack, in which a pinion of the drive engages.
  • the first drive is preferably an electromagnetic linear drive with a primary part which can be energized and a secondary part which interacts electromagnetically with the primary part, the primary part of the first drive preferably being fastened to the first platform and the secondary part of the first drive forming at least part of the first countermass, and / or the second drive is an electromagnetic linear drive having a primary part which can be energized and a secondary part which interacts electromagnetically with the primary part, wherein preferably the primary part of the second drive is fastened to the first platform and the secondary part of the second drive forms at least part of the second countermass.
  • the secondary part is a linear drive with electromagnetic power transmission through an air gap.
  • One of the two parts, preferably the secondary part can be assigned to the counterweight.
  • the secondary part consists of a stator made of permanent magnets and is preferably U-shaped.
  • the energizable primary part protrudes into the secondary part.
  • linear motors are e.g. available as LMC series from the company HIWIN GmbH and are light and dynamic.
  • Embodiments with an ironless primary part (forcer) with epoxy-sputtered coils are preferred herein.
  • the primary part of the drive to which the cable is also connected or which is energized, corresponds to the lighter part and is attached to the first platform. This also has the advantage that only the secondary part, which has no supply line, must be moved dynamically by the primary part.
  • the secondary part of the drive together with the scale is moved, while the primary part together with the reading head is not moved or connected to the first platform.
  • This has the advantage that the signal and power cables do not have to be moved dynamically relative to the first platform.
  • Such a solution is simple, fail-safe, space-saving, cheaper and requires no cable drag.
  • the first drive acts directly on the first coupling mechanism, which transmits the movement of the drive to the first displacement element and the first counterweight
  • the second drive acts directly on the second coupling mechanism, which controls the movement of the second drive to the second Displacement element and the second counterweight transmits.
  • the respective coupling mechanism preferably branches the mechanical drive train beginning at the drive symmetrically (but in opposite directions) into a branch extending to the countermass and into a branch extending to the displacement element.
  • the counterweight does not have to be the same size as that of the displacement element with the jet machining head and the second platform.
  • a coupling e.g. the sliding element moved half as far as a half as heavy counterweight, could also be achieved a mass balance.
  • Such a variant has advantages due to the reduced overall mass of the system.
  • the first drive acts directly on the first displacement element, which transmits the movement via the first coupling mechanism to the first counterweight
  • / or the second drive acts directly on the second displacement element, the movement via the second coupling mechanism to the second counterweight transfers.
  • the shot blasting apparatus can be used even if counterweight and / or coupling mechanism, e.g. for maintenance purposes, are temporarily removed.
  • a rotary drive (e.g., torque motor) drives a pinion to move two toothed linear guides (e.g., racks) in the opposite direction.
  • the one linear guide moves a beam processing head (e.g., laser cutting head) in the same direction via a mechanical connection.
  • a beam processing head e.g., laser cutting head
  • the mechanical coupling is conceivable with a commercially available unit with pinion and double, toothed linear guide but also with other mechanical couplings, such as belt or cable.
  • the principle can also be solved with a linear drive.
  • the linear drive here forms at least a part of the counterweight and is as defined above with respect to the first platform displaceable.
  • the translationally moving mass of the drive can be used as counterweight by the jet machining head (cutting head) is moved in the opposite direction.
  • This can be solved, for example, with a coupling mechanism (pinion racks) described above.
  • the racks are arranged on opposite sides of the pinion and engage in the pinion.
  • the number of parts can be kept low, which has an advantageous effect on the total weight.
  • the axis of rotation of the pinion is fixed to the first platform. This allows a stable construction.
  • the drive is a rotary drive whose axis of rotation coincides with the axis of rotation of the pinion. This solution is particularly space-saving and free of play.
  • the first coupling mechanism of a circulating traction means in particular a belt, a belt, a rope or a chain is formed, the in its course two, in a movement of the traction means in opposite directions moving sections, wherein the first displacement element is connected to one of the two portions of the traction means and the first counterweight is connected to the other portion of the traction means, and / or the second coupling mechanism from a circulating traction means, in particular a belt, a band, a rope or a chain, formed in its course two moving in a movement of the traction means in opposite directions sections, wherein the second displacement element at one of the two portions of the traction means is connected and the second counterweight is connected to the other portion of the traction device.
  • a circulating traction means in particular a belt, a belt, a rope or a chain
  • deflection rollers For deflecting the traction means and for forming two opposing sections deflecting means, in particular deflection rollers may be provided.
  • Traction means in particular in the form of belts, can thus also be used as mechanical couplings.
  • Variants with different drives are conceivable, e.g. Rotary motors or linear drives.
  • linear drives which act as counterweight as described above, a particularly accurate mass balance can be achieved if necessary with additional masses.
  • the first coupling mechanism of a rotatable threaded spindle in particular a ball screw, with two, mutually opposing thread pitch having portions formed, wherein the first displacement element is connected to one of the two sections of the threaded spindle and the first counterweight is connected to the other portion of the threaded spindle, and / or the second coupling mechanism is formed from a rotatable threaded spindle, in particular a ball screw, with two mutually opposing thread pitch having sections, wherein the second displacement element is connected to one of the two sections of the threaded spindle and the second counterweight is connected to the other portion of the threaded spindle.
  • This represents a particularly elegant solution since the first and the fifth linear axis coincide here, as well as the second and the second sixth linear axis coincide. In addition to optimal coupling, this results in excellent mass balance even with strong accelerations.
  • This embodiment is preferably realized with a rotary drive.
  • two objects By turning the spindle with right and left hand thread, two objects (displacement element and counterweight) can be moved in opposite directions. This can be used to balance the cutting head and counterweight.
  • the threaded spindle is held at one end by a rotary drive and driven, while the other end of the threaded spindle is a free end.
  • the coupling mechanism is thus held by the drive, which is stationarily connected to the first platform.
  • the drive assumes a holding function in the present case.
  • the counterweight on the threaded spindle between the drive (rotary drive) and the displacement element is arranged or connected, whereby the best possible use of space is ensured.
  • the threaded spindle is a continuous spindle, which minimizes the design complexity.
  • the first, second, third, fourth, fifth and / or sixth linear axis in the form of a linear guide, in particular a rail implemented.
  • the degrees of freedom of the beam machining head are defined exactly and essentially free of play.
  • the first platform, the second platform, the first and second displacement element and the first and second drive together form a parallel kinematics, whereby a high dynamics can be achieved.
  • the first platform is formed on a carrier which is movable in a plane, preferably along a first linear displacement axis and along a second linear displacement axis, wherein the linear displacement axes are preferably orthogonal to each other.
  • the workpiece support is arranged below the carrier to arrange a particular flat or plate-shaped workpiece below the beam processing head.
  • the invention is not limited to the examples described above, but allows a variety of developments.
  • an integration of a Z-axis transverse to the direction of movement, ie perpendicular to the first to sixth linear axis be provided so that the shot-blasting head relative to the first platform along the Z-axis (vertical) can be moved.
  • the first platform together with the second platform hanging thereon can be moved along the Z-axis (vertically) in the beam-processing device.
  • This method can also be dynamic if only the shot-blast head needs to be moved.
  • the countermeasures can be arranged so that not only the translational forces are avoided, but also resulting moments.
  • the invention forms a highly dynamic Cartesian motion unit for (laser) beam machining or cutting with two (parallel) drives and minimal reaction forces of acceleration forces on the mounting of the movement unit.
  • the first platform may be suspended from the longer and less dynamic axes X-Y-Z.
  • a variety of uses comes about.
  • the Fig. 1 . 2 and 3 show a first embodiment of a beam processing apparatus 100 with a first platform 1, with a second platform 2 movably mounted on the first platform 1 and with a beam processing head 3 held by the second platform 2 for processing a workpiece 5 held on a workpiece support 4 with a jet, in particular a laser beam or water jet.
  • the beam processing device 100 is eg a cutting device for cutting flat workpieces, in particular metal sheets (eg steel sheets).
  • the second platform 2 is connected to the first platform 1 via a first displacement element 21 and a second displacement element 22, wherein the first displacement element 21 is displaceably mounted on the first platform 1 along a first linear axis 11 and the second displacement element 22 on the first platform 1 is slidably mounted along a second linear axis 12.
  • the first linear axis 11 and the second linear axis 12 are inclined to each other, in the present case by 90 °, resulting in a Cartesian motion system.
  • the second platform 2 is slidably mounted on the first displacement element 21 along a third linear axis 13 and slidably mounted on the second displacement element 22 along a fourth linear axis 14.
  • the first linear axis 11 and the fourth linear axis 14 are substantially parallel to each other and the second linear axis 12 and the third linear axis 13 are also substantially parallel to each other.
  • a method of the first displacement element 21 relative to the first platform 1 along the linear axis 11 thus causes a method of the second platform 2 relative to the second displacement element 22 along the linear axis 14.
  • this also applies with regard to the linear axes 12 and 13th
  • the arrangement shown further comprises a first drive 41, which cooperates with the first displacement element 21 to move the first displacement element 21 relative to the first platform 1 along the first linear axis 11, and a second drive 42, which cooperates with the second displacement element 22 to the second displacement element 22 relative to the first platform 1 along the second linear axis 12 to move.
  • a first counterweight 31 is displaceably mounted relative to the first platform 1 along a fifth linear axis 15, and a second counterweight 32 is displaceably mounted relative to the first platform 1 along a sixth linear axis 16.
  • the first linear axis 11 and the fifth linear axis 15 run or stand substantially parallel to one another and the second linear axis 12 and the sixth linear axis 16 run or are substantially parallel to one another.
  • the course of the linear axes is in particular in the plan view of Fig. 3 seen.
  • the first, second, third, fourth, fifth and / or sixth linear axis 11, 12, 13, 14, 15, 16 can be realized in the form of a linear guide, in particular a rail.
  • the first drive 41 which drives the first displacement element 21 relative to the first platform 1, also cooperates with the first counterweight 31 to the first Counterweight 31 relative to the first platform 1 along the fifth linear axis 15 to proceed.
  • a first mechanical coupling mechanism 51 is connected between the first displacement element 21 and the first counterweight 31, which causes a simultaneous movement of the first displacement element 21 and the first counterweight 31 in mutually opposite directions when the first drive 41 is actuated.
  • the second drive 42 which drives the second displacement element 22 relative to the first platform 1, also cooperates with the second counterweight 32 to move the second counterweight 32 relative to the first platform 1 along the sixth linear axis 16.
  • a second mechanical coupling mechanism 52 is connected, which causes a simultaneous movement of the second displacement element 22 and the second counterweight 32 in opposite directions when the second drive 42 is actuated.
  • the drives 41, 42 are rotary drives, e.g. Torque motors. Both drives 41, 42 are seated on the first platform 1, i. the axes of rotation of the rotary drives are stationary with respect to the first platform 1.
  • the first platform 1, the second platform 2, the first and second displacement elements 21, 22 and the first and second drives 41, 42 together form a parallel kinematic system.
  • the first drive 41 is connected to the first coupling mechanism 51 and acts directly on this.
  • the coupling mechanism 51 transmits the movement of the drive 41 to the first displacement element 21 and the first counterweight 31.
  • the second drive 42 acts directly on the second coupling mechanism 52, which then controls the movement of the second drive 42 to the second displacement element 22 and the second Counterweight 32 transmits.
  • the first coupling mechanism 51 is formed from at least one pinion 53 and two racks 54, 55 cooperating with the pinion 53, which move in opposite directions upon rotation of the pinion 53.
  • one of the racks 54 on the first displacement element 21 and the other rack 55 is formed on the first counterweight 31 or provided.
  • the second coupling mechanism 52 is constructed analogously to the first coupling mechanism 51 in the illustrated example.
  • racks 54, 55 are arranged on opposite sides of the pinion 53 as in the example shown and engage in the pinion 53, resulting in an opposite movement of displacement element 21, 22 and associated counterweight 31, 32 results.
  • the respective pinion 53 is arranged such that its axis of rotation coincides with the axis of rotation of the corresponding drive 41 or 42 and thus also is stationary relative to the first platform 1.
  • FIGS. 4 and 5 show a second embodiment of the invention. Since that is based on the FIGS. 1 to 3 described basic principle, in particular the course of the linear axes, also in the embodiment of the FIGS. 4 and 5 is the same, to avoid redundancy, a further explanation is omitted.
  • the first coupling mechanism 51 is formed by a rotatable threaded spindle 59, in particular a ball screw.
  • the threaded spindle 59 has two sections 60, 61 which have opposing thread pitches.
  • the first displacement element 21 at one of the two portions 61 of the threaded spindle 59 via a threaded nut (not shown), in particular a ball screw nut, connected.
  • the first counterweight 31 is connected to the other, a counter-rotating threaded portion having portion 60 of the threaded spindle 59 via a threaded nut (not shown), in particular a ball screw nut, connected.
  • a rotation of the threaded spindle 59 about its longitudinal axis now causes the first displacement element 21 and the first counterweight 31 to move away from each other in an opposite direction or relative to one another, as a result of which mass compensation takes place.
  • the first and fifth linear axes 11, 15 can coincide in this embodiment, as can the second and the sixth linear axis 12, 16.
  • the threaded spindle 59 is held and driven at one end of the first drive 41, which is a rotary drive, while the other end of the threaded spindle 59 is a free end.
  • the second coupling mechanism 52 is formed in the example shown analogous to the first coupling mechanism 51.
  • FIGS. 6 . 7 and 8th each show in perspective view, in plan view and in side view a third embodiment of the invention. Again, a further explanation of the basic principle is omitted and discussed in more detail only on the specifics of this embodiment.
  • the first drive 41 and the second drive 42 are each designed as a linear drive, ie, the movement emanating from them is a translational movement.
  • the first embodiment FIGS. 1 to 3
  • a part of the first drive 41 is displaceable relative to the first platform 1 along the fifth linear axis 15.
  • the first drive 41 not only serves for driving the first displacement element 21 and the first countermass 31, but at the same time forms part of the first counterweight 31 or even the entire first counterweight 31.
  • a part of the first drive 41 is thus as counterweight or as part the counterweight relative to the first platform 1 displaceable (along the fifth linear axis).
  • the first drive 41 cooperates with the first platform 1 insofar as a part of the first drive 41 (eg via a primary part, an actuator end, a rotatable pinion, etc.) interacts with a structure of the first platform 1 or on a structure of the first platform 1 first platform 1 attacks or is attached to the first platform 1.
  • the first drive 41 is an electromagnetic linear drive with a current-carrying primary part 6 and an electromagnetic with the primary part 6 (via an air gap) cooperating secondary part 17.
  • the primary part 6 is attached to the first platform 1 and the secondary part 17 forms the first counterweight 31st
  • the secondary part 17 consists of an elongated, U-shaped cross-section having stator, which preferably contains permanent magnets.
  • stator which preferably contains permanent magnets.
  • the bestrombare primary part 6 which contains primary coils.
  • Fig. 9 shows a fourth embodiment, in its explanation, in turn, the above-described inventive basic principle is assumed.
  • the first coupling mechanism 51 is formed from a circulating traction means 56, in particular a belt, a belt, a rope or a chain, which in its course has two sections 57, 58 which move in opposite directions upon movement of the traction means 56. This is achieved by appropriately arranged pulleys on which the traction device undergoes a change of direction.
  • the first displacement element 21 is connected to one of the two sections 57 of the traction means 56 and the first counterweight 31 is connected to the other (oppositely moved) section 58 of the traction means 56.
  • the second coupling mechanism 52 is substantially similar to the first coupling mechanism 51, except that the first coupling mechanism 51 is formed to enclose a support of the first platform 1 from three sides.
  • the great advantage of this embodiment is therefore that the coupling mechanism due to the flexibility and deflectability of the traction means 56 by deflection (such as those in Fig. 9 shown pulleys) can be easily adapted to the basic design, resulting in very space-saving arrangements.
  • Fig. 9 are the drives 41, 42 rotary actuators, each attacking a deflection roller or whose respective axis of rotation coincides with the axis of rotation of the respective deflection roller.
  • FIG. 10 show in perspective view and in two side views a further embodiment of the invention.
  • the drives 41, 42 designed here as linear drives, which form at least a portion of the counter-masses 31, 32.
  • the first drive 41 is seated on the traction means 56 on the section 58 of the traction means 56 and is thus displaceably mounted along the fifth linear axis 15 relative to the first platform 1.
  • the first drive 41 takes over the additional Function of the first counterweight 31, whereby during a movement of the first displacement element 21 including held by this second platform 2 together with the beam processing head 3, a mass balance by the opposite movement of the drive 41 as counterweight 31 takes place.
  • an electromagnetic linear drive with a primary part 6 (from energizable primary coils) and a secondary part 17 (preferably of permanent magnets).
  • the primary part 6 is attached to the first platform 1 and the secondary part 17 forms in each case the corresponding counterweight 31 or 32 (FIG. Figures 11 and 12 ).
  • the second drive 42 is analogous to the first drive 41 is formed or connected to the movement unit.
  • Fig. 13 finally shows in a schematic representation a beam processing device 100 as a whole with a base frame 8, on which a carrier 9 along a linear displacement axis X is arranged movable.
  • the first platform 1 (only shown by way of example in the form of a housing and without further parts of the movement unit) is arranged so as to be movable along a linear displacement axis Y, which is orthogonal to the displacement axis X.
  • a workpiece support 4 is arranged, which carries a workpiece 5 to be machined.
  • the first platform 1 is arranged on a Y-carriage 7 so that the first platform 1 as a whole is perpendicular relative to the carrier 9 in the Z1-direction, which in this example is perpendicular to the plane spanned by the displacement axis X and the displacement axis Y can be positioned to the workpiece 5.
  • the first platform 1 carries, via the second platform 2, a shot-blasting head 3, e.g. a laser beam machining head or a fluid jet machining head, by which a beam exit axis is defined, along which emerges during the processing of the beam (beam exit opening).
  • a shot-blasting head 3 e.g. a laser beam machining head or a fluid jet machining head, by which a beam exit axis is defined, along which emerges during the processing of the beam (beam exit opening).
  • the beam processing head 3 is mounted such that various movements can be performed with it.
  • a further, “inner” Z-axis in addition to the in Fig. 3 drawn Z-axis transverse to the direction of movement (ie, perpendicular to the first to sixth linear axis) of the displacement elements and the countermeasures are provided.
  • the beam machining head 3 can be moved relative to the first platform 1 along this further Z axis.
  • This variant is thus characterized in that the beam machining head 3 can be moved relative to the first platform 1 along a linear axis that is perpendicular to the first linear axis 11 and perpendicular to the second linear axis 12. As a result, an exact vertical fine adjustment of the jet machining head 3 relative to the underlying workpiece.
  • the invention is not limited to the illustrated embodiments, but can be modified and expanded many times.
  • the first drive can act directly on the first displacement element, which transmits the movement via the first coupling mechanism to the first counterweight
  • the second drive can act directly on the second displacement element, the movement via the second coupling mechanism to the second Counterweight transfers. It would also be possible in principle to design the first displacement element together with the first drive and the first counterweight differently than the second displacement element together with the second drive and the second counterweight.

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  • Physics & Mathematics (AREA)
  • Optics & Photonics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Laser Beam Processing (AREA)
EP12179304.6A 2012-08-03 2012-08-03 Dispositif de traitement par rayonnement Withdrawn EP2692481A1 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105921899A (zh) * 2016-06-12 2016-09-07 广州敏惠汽车零部件有限公司 一种行李架总成件自动焊接专机
CN105921898A (zh) * 2016-06-12 2016-09-07 广州敏惠汽车零部件有限公司 一种行李架brkt件与铁柱自动焊接专机
WO2019046746A1 (fr) * 2017-08-31 2019-03-07 Laser Mechanisms, Inc. Effecteur d'extrémité de bras robotique

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JPH01193134A (ja) 1988-01-27 1989-08-03 Komatsu Ltd スライドテーブルを有する構造物のカウンターバランス移動装置
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EP1312441A1 (fr) 2001-11-15 2003-05-21 Mitsubishi Heavy Industries, Ltd. Machine-outil
EP1294544B1 (fr) 2000-06-30 2005-08-24 Franco Sartorio Machine-outil et dispositif manipulateur agence de maniere a etre monte sur une telle machine
WO2006075209A2 (fr) 2005-01-13 2006-07-20 Prima Industrie S.P.A. Machine-outil laser
EP1793963B1 (fr) 2004-09-28 2008-04-16 PRIMA INDUSTRIE S.p.A. Poinçonneuse laser
EP1724054B1 (fr) 2005-05-18 2008-11-19 Franco Sartorio Mécanisme d'équilibrage pour machine outil
US7767932B2 (en) 2007-06-29 2010-08-03 Trumpf, Inc. High dynamics laser processing machine
EP2283963A1 (fr) 2009-07-27 2011-02-16 SALVAGNINI ITALIA S.p.A. Manipulateur à faible inertie pour découper par laser des tôles métalliques minces
DE102009039203A1 (de) 2009-08-27 2011-03-17 Andreas Ehlerding Einrichtung zur Kompensation von Drehmomenten, die durch Beschleunigung von redundanten Zusatzachsen bei Mess- und Werkzeugmaschinen entstehen mittels einer Mehrzahl von koordiniert linear bewegbarer Ausgleichsmassen
DE102009039201B3 (de) 2009-08-27 2011-04-07 Andreas Ehlerding Einrichtung zur Kompensation von Beschleunigungskräften mittels Impulsentkopplung bei Mess- und Werkzeugmaschinen in mindestens einer translatorisch wirksamen Maschinenachse
EP1758003B1 (fr) 2005-08-16 2011-11-09 PRIMA INDUSTRIE S.p.A. Méthode pour la commande de systèmes pourvus d'actionneurs redondants
WO2012069181A1 (fr) * 2010-11-26 2012-05-31 Wenzel Scantec Gmbh Équilibrage de poids sur une machine de mesure de coordonnées

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JPS6268208A (ja) * 1985-09-19 1987-03-28 Toshiba Corp 縦形移動テ−ブル装置
JPH01193134A (ja) 1988-01-27 1989-08-03 Komatsu Ltd スライドテーブルを有する構造物のカウンターバランス移動装置
DE10027775A1 (de) * 2000-05-23 2002-02-14 Baumueller Nuernberg Gmbh Aktive Kompensation von Kraftrückwirkungen mechanisch beschleunigter Maschinenteile
US7886629B2 (en) 2000-06-30 2011-02-15 Franco Sartorio Machine tool and manipulator device adapted to be mounted on such machine
EP1294544B1 (fr) 2000-06-30 2005-08-24 Franco Sartorio Machine-outil et dispositif manipulateur agence de maniere a etre monte sur une telle machine
EP1312441A1 (fr) 2001-11-15 2003-05-21 Mitsubishi Heavy Industries, Ltd. Machine-outil
EP1793963B1 (fr) 2004-09-28 2008-04-16 PRIMA INDUSTRIE S.p.A. Poinçonneuse laser
WO2006075209A2 (fr) 2005-01-13 2006-07-20 Prima Industrie S.P.A. Machine-outil laser
EP1838486A2 (fr) 2005-01-13 2007-10-03 PRIMA INDUSTRIE S.p.A. Machine-outil laser avec une structure pour deplacement x-y avec des masses d'equilibrage
US7910857B2 (en) 2005-01-13 2011-03-22 Prima Industrie S.P.A. Laser machine tool
EP1724054B1 (fr) 2005-05-18 2008-11-19 Franco Sartorio Mécanisme d'équilibrage pour machine outil
EP1758003B1 (fr) 2005-08-16 2011-11-09 PRIMA INDUSTRIE S.p.A. Méthode pour la commande de systèmes pourvus d'actionneurs redondants
US7767932B2 (en) 2007-06-29 2010-08-03 Trumpf, Inc. High dynamics laser processing machine
EP2283963A1 (fr) 2009-07-27 2011-02-16 SALVAGNINI ITALIA S.p.A. Manipulateur à faible inertie pour découper par laser des tôles métalliques minces
DE102009039203A1 (de) 2009-08-27 2011-03-17 Andreas Ehlerding Einrichtung zur Kompensation von Drehmomenten, die durch Beschleunigung von redundanten Zusatzachsen bei Mess- und Werkzeugmaschinen entstehen mittels einer Mehrzahl von koordiniert linear bewegbarer Ausgleichsmassen
DE102009039201B3 (de) 2009-08-27 2011-04-07 Andreas Ehlerding Einrichtung zur Kompensation von Beschleunigungskräften mittels Impulsentkopplung bei Mess- und Werkzeugmaschinen in mindestens einer translatorisch wirksamen Maschinenachse
WO2012069181A1 (fr) * 2010-11-26 2012-05-31 Wenzel Scantec Gmbh Équilibrage de poids sur une machine de mesure de coordonnées

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105921899A (zh) * 2016-06-12 2016-09-07 广州敏惠汽车零部件有限公司 一种行李架总成件自动焊接专机
CN105921898A (zh) * 2016-06-12 2016-09-07 广州敏惠汽车零部件有限公司 一种行李架brkt件与铁柱自动焊接专机
WO2019046746A1 (fr) * 2017-08-31 2019-03-07 Laser Mechanisms, Inc. Effecteur d'extrémité de bras robotique

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